JP2013061073A - Damping valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damping valve capable of surely performing a damping force adjustment and a failsafe function.SOLUTION: This damping valve V1 includes: a valve element 1 arranged in the middle of a flow passage P and applying resistance to a passing fluid; a solenoid S applying thrust in a direction for limiting the flow passage area to a valve element 2 in the valve element 1; and an elastic body 3 applying thrust in a direction for maximizing the flow passage area to the valve element 2. A fail valve 4 disposed in series to the valve element 1 is arranged in the middle of the flow passage P. The fail valve 4 has an opening position for opening the flow passage P and a fail position for reducing the flow passage area, and takes the fail position when a supply current to the solenoid S becomes a predetermined value or smaller, so that the valve element and the fail valve are driven independently of each other by a single solenoid.

Description

  The present invention relates to a damping valve provided in the middle of a discharge passage in a shock absorber that discharges fluid from a cylinder to a reservoir via a discharge passage during expansion and contraction.

  Conventionally, as a damping valve provided in the middle of a discharge passage in a shock absorber that discharges fluid from a cylinder to a reservoir via a discharge passage during expansion and contraction, for example, it is fixed to the shaft core of a movable iron core driven by a solenoid and A shaft body provided with an annular groove, a biasing spring for urging the shaft body upward against the thrust of the solenoid, and a hole into which the shaft body is inserted and having a thickness narrower than the width of the annular groove The plate is configured to be configured to be opposed to the outer periphery of the annular groove, and the upper edge of the hole in the plate and the upper edge of the annular groove form a valve portion that functions during normal operation. The lower edge of the hole in the plate and the lower edge of the annular groove form an emergency valve portion that functions during an emergency operation.

  In this damping valve, the solenoid is excited to place the shaft body in a neutral position within a range where the plate faces the outer periphery of the annular groove (a position where the plate is disposed in the middle in the axial direction with respect to the annular groove). ), The flow passage area in the valve portion formed by the upper edge of the plate hole and the upper edge of the annular groove is reduced to the lower edge of the plate hole and the lower edge of the annular groove. When the shaft body is moved downward from the neutral position by the biasing spring without exciting the solenoid, the flow area in the valve section is reduced in the emergency valve section. It is designed to be larger than the channel area.

  That is, in a situation where the system operates normally, the position of the shaft body is arranged above the neutral position by adjusting the amount of current supplied to the solenoid, and the flow passage area in the valve portion is adjusted, and the damping force is applied by the valve portion. On the other hand, in a situation where the system does not operate normally and power cannot be supplied to the solenoid, the shaft body is disposed at the lowest position by the biasing spring and the damping force is generated by the emergency valve portion ( For example, see Patent Document 1).

Japanese Patent No. 3064964

  By the way, in this conventional damping valve, adjustment of the flow path area in the emergency valve portion at the time of failure when the solenoid cannot be excited is performed by the position of the stopper disposed above the movable iron core. Is capable of adjusting the flow passage area in the emergency valve section in a stepless manner, which can be viewed from the movable iron core by a feed screw mechanism.

  As described above, in the conventional damping valve, the shaft body driven by a single solenoid is used to determine the control of the valve portion during normal operation and the flow area of the emergency valve portion during failure. Therefore, when setting the movement limit above the movable iron core with the stopper and determining the flow passage area of the emergency valve part, the stopper restricts the plate in a state where it is disposed above the neutral position with respect to the annular groove. Even in the failed state, the flow area in the valve section is smaller than the flow area in the emergency valve section, and the emergency valve section does not function, and the flow area adjustment width in the valve section is reduced and attenuated. The force adjustment cannot be performed satisfactorily.

  Therefore, the present invention has been developed to improve the above-described problems, and an object of the present invention is to provide a damping valve that can reliably perform damping force adjustment and fail-safe.

In order to solve the above-described object, the problem-solving means in the present invention includes a valve element that is provided in the middle of the flow path to provide resistance to the fluid passing therethrough, and in a direction that limits the flow area to the valve body in the valve element. In a damping valve having a solenoid that gives thrust and an elastic body that gives thrust to the valve body in the direction that maximizes the flow path area, a fail valve that is arranged in series with the valve element is provided in the middle of the flow path, The fail valve has an open position that opens the flow path and a fail position that reduces the flow path area. When the supply current to the solenoid falls below a predetermined value, the fail valve takes the fail position. And are driven independently.

  In this damping valve, the valve element and the fail valve are independently driven by a single solenoid, and when the supply current to the solenoid exceeds a predetermined value, only the valve element restricts the flow path and fails. Does not affect the flow path, and conversely, when the current supplied to the solenoid is less than the predetermined value, only the fail valve restricts the flow path so that the valve element does not affect the flow path. Therefore, the valve element and the fail valve do not interfere with each other, and the damping force adjustment and the fail safe can be reliably performed.

  Therefore, even if adjusting the initial load of the spring, which is an elastic body that gives thrust to the valve body in the valve element, to compensate for the product-to-product variation due to tolerances, etc., there is no effect on the fail valve. Since it does not affect the damping force at the time, it is possible to eliminate variations in the product at the time of failure and normal operation.

It is sectional drawing of the damping valve in one embodiment. It is sectional drawing of the buffer with which the damping valve of one Embodiment was applied. It is the figure which showed the magnetic path of the solenoid in the damping valve of one Embodiment. It is the figure which showed the relationship between the electric current supplied to a solenoid, and damping force. It is sectional drawing of the damping valve in other embodiment.

  The present invention will be described below based on the illustrated embodiment. FIG. 1 is a cross-sectional view of a damping valve according to an embodiment. FIG. 2 is a sectional view of a shock absorber to which the damping valve of one embodiment is applied. FIG. 3 is a diagram illustrating a magnetic path of a solenoid in the damping valve according to the embodiment. FIG. 4 is a diagram showing the relationship between the current supplied to the solenoid and the damping force. FIG. 5 is a cross-sectional view of a damping valve according to another embodiment.

  The damping valve of the present invention will be described below based on the embodiment shown in the drawings. As shown in FIG. 1, the damping valve V <b> 1 in one embodiment has a flow path area in the valve element 1 that is provided in the middle of the flow path P and provides resistance to the fluid passing therethrough, and the valve body 2 in the valve element 1. A solenoid S that gives thrust in the limiting direction, a spring 3 as an elastic body that gives thrust to the valve body 2 in the direction that maximizes the flow path area, and the valve element 1 are arranged in series in the flow path P. It is provided with a fail valve 4 and is applied to a shock absorber D. The shock absorber D generates a damping force by applying resistance to the fluid passing through the damping valve V1 during expansion and contraction.

  The shock absorber D to which the damping valve V1 is applied includes, for example, as shown in FIG. 2, a cylinder 5, a piston 6 that is slidably inserted into the cylinder 5, and a piston that is moved and inserted into the cylinder 5. 6, a rod 7 connected to the cylinder 5, a rod side chamber 8 and a piston side chamber 9 defined by a piston 6 inserted into the cylinder 5, and a pipe 11 that covers the outer periphery of the cylinder 5 and forms a discharge passage 10 between the cylinder 5. And an outer cylinder 13 that covers the outer periphery of the pipe 11 and forms a reservoir 12 with the pipe 11. The rod side chamber 8, the piston side chamber 9, and the reservoir 12 contain hydraulic oil and the like. The reservoir 12 is filled with gas in addition to the hydraulic oil. In addition to hydraulic fluid, the fluid can be used as long as it can exhibit a damping force.

  In the case of the shock absorber D, only the flow of the working oil from the reservoir 12 to the piston side chamber 9 and the flow of the working oil from the piston side chamber 9 to the rod side chamber 8 provided in the piston 6 is allowed. The discharge passage 10 communicates the piston side chamber 9 and the reservoir 12, and the damping valve V1 is provided in the middle of the discharge passage 10 by connecting the flow path P to the discharge passage 10. It has been.

  Therefore, in the shock absorber D, when the compression operation is performed, the piston 6 moves downward in FIG. 2 to compress the piston side chamber 9, and the hydraulic oil in the piston side chamber 9 passes through the in-cylinder passage 15 to the rod side chamber. Move to 8. At the time of this compression operation, the rod 7 enters the cylinder 5, so that the hydraulic oil corresponding to the rod penetration volume becomes excessive in the cylinder 5, and the excess hydraulic oil is pushed out of the cylinder 5 and is stored in the reservoir 12 through the discharge passage 10. Is discharged. The shock absorber D increases the pressure in the cylinder 5 by exerting a resistance to the flow of hydraulic oil that passes through the discharge passage 10 and moves to the reservoir 12 by the damping valve V <b> 1, and exhibits a compression side damping force.

  On the contrary, when the shock absorber D is extended, the piston 6 moves upward in FIG. 2 to compress the rod side chamber 8, and the hydraulic oil in the rod side chamber 8 moves to the reservoir 12 through the discharge passage 10. To do. During this compression operation, the piston 6 moves upward to increase the volume of the piston side chamber 9, and hydraulic oil commensurate with this expansion is supplied from the reservoir 12 via the suction passage 14. Then, the shock absorber D increases the pressure in the rod side chamber 8 by exerting a resistance to the flow of the hydraulic oil that passes through the discharge passage 10 and moves to the reservoir 12 by the damping valve V1, and exhibits the extension side damping force. .

  As can be understood from the above description, when the shock absorber D exhibits an expansion / contraction operation, the hydraulic oil is always discharged from the cylinder 5 through the discharge passage 10 to the reservoir 12, and the hydraulic oil is discharged to the piston side chamber 9 and the rod side chamber 8. The uniflow type shock absorber that circulates in the reservoir 12 in a one-way manner in order, and the damping force on both sides of the pressure expansion is generated by a single damping valve V1. In addition, since the cross-sectional area of the rod 7 is set to ½ of the cross-sectional area of the piston 6, the amount of hydraulic oil discharged from the cylinder 5 can be set equally on both sides of the pressure expansion with the same amplitude. By setting the resistance applied to the flow by the damping valve V1 to be the same, the damping force on the expansion side and the compression side can be set to be the same.

  Subsequently, the damping valve V1 includes a hollow valve housing 16 fitted with a sleeve 11a provided at an opening of the pipe 11 and provided with a flow path P, a valve body 2 accommodated in the valve housing 16, and a solenoid. S, a spring 3 that applies thrust to the valve body 2 in a direction that maximizes the flow path area, a spring 17 that serves as a blocking elastic body that applies thrust to the valve body 2 in a direction that limits the flow path area, and a fail valve 4 And is configured.

  As shown in FIG. 1, the valve housing 16 includes a horizontal hole 16 a along the axis and a vertical hole 16 b that communicates with the horizontal hole 16 a, and the outer periphery of the tip that is the left end in the figure is fitted to the sleeve 11 a of the pipe 11. The left end opening of the horizontal hole 16a faces the discharge passage 10 formed between the pipe 11 and the cylinder 5, and the vertical hole 16b faces the reservoir 12. The horizontal hole 16a and the vertical hole 16b A flow path P is formed.

  Further, the valve housing 16 is formed at the inner edge of the small inner diameter portion 16c by providing a small inner diameter portion 16c in the middle of the horizontal hole 16a and on the left side in FIG. An annular valve seat 18 is provided, and on the outer periphery, a flange 16d is provided on the left side in FIG. A large outer diameter portion 16e is provided on the right side in FIG.

  Further, a seal ring 19 is attached to the outer periphery of the fitting portion of the valve housing 16 to the sleeve 11 a, and the space between the discharge passage 10 and the reservoir 12 is sealed. And the reservoir 12 are not communicated with each other.

  Further, the flange 16d of the valve housing 16 is fitted to the inner periphery of the cylinder 13b attached to the opening 13a provided on the side portion of the outer cylinder 13, and is brought into contact with the step portion 13c provided on the inner periphery of the cylinder 13b. ing. The cylinder 13b is provided with a screw part (not shown) on the outer periphery of the end, and a bottomed cylindrical case 20 containing a solenoid S is screwed to the cylinder 13b.

  The case 20 includes a cylindrical portion 20a, a bottom portion 20b fixed by crimping the opening end of the cylindrical portion 20a, and a solenoid bobbin that is provided on the inner peripheral side of the cylindrical portion 20a and holds the winding 21 in the solenoid S. The flange 20c is configured to hold the flange 16d of the valve housing 16 and the non-magnetic spacer 23 between the flange 20c and the step portion 13c of the cylinder 13b. Fixed to. A through hole 16f is formed in the flange 16d so that the communication with the reservoir 12 of the flow path P is not interrupted by the flange 16d even if fixed in this way.

  The solenoid S includes the above-described bottomed cylindrical case 20, an annular solenoid bobbin 22 that holds the winding 21 and is fixed to the bottom of the case 20, and has a bottomed cylindrical shape and an inner periphery of the solenoid bobbin 22. The first fixed iron core 24 fitted to the inner circumference of the solenoid bobbin 22, the cylindrical second fixed iron core 25 fitted to the inner circumference of the solenoid bobbin 22, and the first fixed iron core fitted to the inner circumference of the solenoid bobbin 22 A non-magnetic cylindrical spacer 26 interposed between the iron core 24 and the second fixed iron core 25; a bottomed cylindrical movable iron core 27 disposed on the inner peripheral side of the first fixed iron core 24; In addition to the movable iron core 27, a cylindrical fail valve element 28 that functions as another movable iron core is slidably mounted on the outer periphery of the large outer diameter portion 16 e of the valve housing 16.

  The bottomed cylindrical movable core 27 is slidably inserted into the inner periphery of the first fixed core 24 with the opening end side of the cylinder facing the inner side of the first fixed core 24, and the first fixed 1 even if it enters the first fixed iron core 24 until it comes into contact with a non-magnetic washer 29 provided at the bottom of the iron core 24, the bottom side surface on the left in FIG. 1 slightly opposes the inner periphery of the second fixed iron core 25. It is designed to be placed in close proximity. Further, a through hole 27 a is provided in the wall thickness of the movable iron core 27 so that the space partitioned by the first fixed iron core 24 and the movable iron core 27 is not sealed.

  Further, a spring 17 serving as a blocking elastic body is interposed between the movable iron core 27 and the first fixed iron core 24, and thrust is applied in a direction away from the first fixed iron core 24 by the spring 17. The spring 17 is supported by a spring receiver 30a provided at the tip of a spring force adjusting screw 30 as an adjusting member whose right end in FIG. 1 is screwed into the shaft core portion of the first fixed iron core 24. The spring force adjusting screw 30 is By moving the first fixed iron core 24 back and forth, the support position of the spring 17 can be changed to the left and right in FIG. In the case of this embodiment, the spring force adjusting screw 30 can be operated only before the bottom portion 20b of the case 20 is crimped and fixed to the opening end of the cylindrical portion 20a. If a fixing method in which the bottom portion 20b is detachable when the bottom portion 20b is fixed to the cylindrical portion 20a is adopted, the time when the spring force adjusting screw 30 can be operated is not limited to before the bottom portion 20b is fixed.

  The second fixed iron core 25 has a cylindrical shape, the opening end on the first fixed iron core 24 side is tapered so as to be inclined on the inner peripheral side, and the magnetic flux generated when the winding 21 is energized is the inner right end. The shape of the left end in FIG. 1 of the non-magnetic spacer 26 interposed between the second fixed core 25 and the first fixed core 24 is the second fixed core 25. The shape matches the taper.

  As described above, in this solenoid S, the magnetic path is formed so as to pass through the first fixed iron core 24, the movable iron core 27, and the second fixed iron core 25, as shown in FIG. When 21 is excited, the movable iron core 27 disposed closer to the first fixed iron core 24 is attracted to the second fixed iron core 25 side, and a thrust toward the left side in FIG. Yes.

  As shown in FIG. 1, the bottom of the movable iron core 27 is in contact with the valve body 2 of the valve element 1 so that the thrust of the spring 17 is transmitted to the valve body 2 and the solenoid S At the time of excitation, a thrust in a direction toward the left side in FIG. 1 can be applied to the valve body 2 via the attracted movable iron core 27. The movement limit of the movable iron core 27 to the left side in FIG. 1, which is the valve body 2 side, is fitted to the outer periphery of the right end of the valve housing 16 and the movement to the left is restricted by the large outer diameter portion 16e. It is regulated by a cylindrical stopper 31 made of a magnetic material. By providing the washer 29 and the stopper 31 with synthetic resin or the like, it is possible to suppress the generation of impact and sound when the movable iron core 27 is abutted.

  In the case of this embodiment, the valve body 2 extends from the left end of the large diameter portion 2a and the large diameter portion 2a slidably in contact with the inner periphery of the right end of the valve housing 16 in FIG. The small-diameter portion 2b facing each other and a poppet-type valve head 2c formed at the left end of the small-diameter portion 2b are configured to open and close the flow path P when the valve head 2c is seated on and off the valve seat 18. It can be done. In the case of this valve body 2, the small diameter portion 2 b forms a gap with the inner periphery of the valve housing 16, so that the valve body 2 does not block the vertical hole 16 b. Yes.

  A spring 3 is interposed between the left end of the large diameter portion 2a of the valve body 2 and the right end of the small inner diameter portion 16c of the valve housing 16, and the spring 3 attaches the valve body 2 to the valve seat. The thrust is exerted in the direction away from 18, and the thrust is applied to the valve body 2 in the direction that maximizes the flow path area in the flow path P.

  Accordingly, the valve body 2 is sandwiched between the spring 3 and the spring 17 via the movable iron core 27, and the thrust in the direction that maximizes the flow path area of the flow path P acts by the spring 3 and is movable in the opposite direction. The thrust in the direction of restricting the flow path of the flow path P is acted by the spring 17 through the iron core 27, and the thrust of the spring 3 as an elastic body is cut off when the valve body 2 is not energized to the solenoid S. The valve body 2 is pushed into the first fixed iron core 24 until the movable iron core 27 comes into contact with the washer 29 so as to match or exceed the thrust force of the spring 17 which is an elastic body, and the valve body 2 is moved to the position where the flow path P is fully opened. It has come to retreat from.

  Here, as can be understood from the above description, the spring 3 and the spring 17 are arranged in series. Therefore, when the support position of the spring 17 is adjusted by the spring force adjusting screw 30, the length of the spring 17 in the compressed state is set. That is, not only can the compression length be changed, but also the compression length of the spring 3 can be adjusted, and the initial thrust that these springs 3 and 17 act on the valve body 2 can be adjusted. ing.

  By adjusting this initial thrust, the position of the valve body 2 with respect to the amount of current supplied to the solenoid S, that is, the flow path area in the valve element 1 can be adjusted. The adjusting member is not limited to the above-described spring force adjusting screw 30 as long as the supporting position of the spring 17 can be adjusted in the axial direction.

  Returning, the second fixed iron core 25 in the solenoid S protrudes leftward in FIG. 1 from the solenoid bobbin 22, and a spacer 23 is fitted to the left outer periphery of the second fixed iron core 25. Specifically, the spacer 23 is cylindrical and includes a flange 23 a on the inner periphery of the right end, and the inner periphery of the flange 23 a is fitted to the outer periphery of the second fixed iron core 25. The spacer 23 is also fitted to the inner periphery of a cylinder 13b provided on the outer cylinder 13, and is sealed between the spacer 23 and the cylinder 13b by a seal ring 32 attached to the outer periphery.

  The fail valve 4 includes a fail valve body 28 slidably mounted on the outer periphery of the large outer diameter portion 16e of the valve housing 16, and a fail elastic body interposed between the fail valve body 28 and the flange 23a of the spacer 23. It is configured to include a spring 33.

  The fail valve body 28 has a cylindrical shape, a flange 28a provided on the outer peripheral side, an annular protrusion 28b facing the right end surface in FIG. 1 of the flange 16d of the valve housing 16, and an orifice 28c communicating the inner periphery and the outer periphery. 1 and a through hole 28d that opens from the right end in FIG. 1 and communicates with the orifice 28c. A flange 16d of the valve housing 16 is provided by a spring 33 interposed between the flange 28a and the flange 23a of the spacer 23. Thrust is always given to the side.

  The right end of the fail valve body 28 faces the left end of the second fixed iron core 25, and as shown in FIG. 3, the magnetic path is the second fixed iron core 25, the fail valve body 28, the valve housing 16, It is formed so as to pass through the cylinder 13 b and the case 20. As described above, in the solenoid S, when the winding 21 is excited, the fail valve body 28 is attracted to the second fixed iron core 25, and thrust toward the right side in FIG. It is supposed to be. When the supply current to the solenoid S exceeds a predetermined value, the thrust acting on the fail valve body 28 by the solenoid S overcomes the thrust of the spring 33 and is attracted to the second fixed iron core 25 to open the flow path P to the maximum. .

  On the other hand, when the supply current to the solenoid S becomes a predetermined value or less, the thrust acting on the fail valve body 28 by the solenoid S cannot overcome the thrust of the spring 33, and the fail valve body 28 does not connect the annular protrusion 28b to the valve. The flow path area is limited by contacting the flange 16d of the housing 16. At this time, the orifice 28c of the fail valve body 28 faces the flow path P and communicates with the flow path P only through the orifice 28c, so that the flow path area is limited to the flow area of the orifice 28c.

  Therefore, when the supply current to the solenoid S exceeds a predetermined value, the fail valve 4 takes an open position for opening the flow path P. Conversely, when the supply current to the solenoid S is equal to or less than the predetermined value, the orifice 28c. The fail position which connects the flow path P only through this is taken.

  Even if the fail valve body 28 is in close contact with the second fixed iron core 25, the through hole 28d is not closed by the end portion of the second fixed iron core 25, so that the communication state is maintained. Even when the second fixed iron core 25 is in close contact with the second fixed iron core 25, the space in which the movable iron core 27 is accommodated is not blocked, and the valve body 2 is locked and cannot move. Be blocked.

  As shown in FIG. 4, the damping valve V1 configured as described above has a current in a range from I2 to I3 exceeding a predetermined value I1, as shown in FIG. The current supply to the solenoid S is stopped at the time of failure. In addition, at the time of failure, as a matter of course, when current cannot be supplied, current supply is not performed even if current can be supplied to the solenoid S. Also, I3, which is the upper limit of the current value during normal operation, is determined by the rating of the solenoid S, and the current value I1 at which the fail valve 4 switches to the fail position is not set as the lower limit of the range during normal operation. Prevents the fail valve 4 from being switched to the fail position when it is desired to operate normally because the supply current to the solenoid S becomes oscillating or insufficient due to the stability of the power supply voltage or noise. Therefore, a margin for preventing malfunction is provided between the predetermined value I1 and the lower limit current value I2 during normal operation.

  First, the normal operation will be described. During normal operation, current is supplied to the solenoid S in the range of I2 to I3, which is in the range of the current value exceeding the predetermined value I1, so that the fail valve 4 is in a state where the flow path P is opened. On the other hand, in the valve element 1, the degree of opening or the valve opening pressure of the flow path P of the valve body 2 is adjusted by the thrust toward the valve seat 18 received from the solenoid S.

  When the shock absorber D expands and contracts, the hydraulic oil pushed out from the cylinder 5 through the discharge passage 10 moves to the reservoir 12 through the valve element 1 in the damping valve V1. A resistance is given to the flow of the hydraulic oil by the valve element 1, the pressure in the cylinder 5 is increased, and a damping force is generated.

  This damping force can be changed according to the magnitude of the resistance provided by the valve element 1, and specifically, the resistance given by the valve element 1 when the supply current to the solenoid S becomes the current value I2 is minimized. Thus, the shock absorber D generates a minimum soft damping force. Conversely, when the current supplied to the solenoid S reaches the current value I3, the resistance provided by the valve element 1 is maximized. By generating the maximum hard damping force and changing the amount of current supplied to the solenoid S, the damping force of the shock absorber D can be adjusted steplessly between soft and hard.

  In turn, since the solenoid S is not energized at the time of failure, the valve element 2 in the valve element 1 is retreated to the right in FIG. 1 by the spring force of the spring 3 against the spring 17 to open the flow path P. On the contrary, the fail valve body 28 in the fail valve 4 is pressed toward the flange 16d side of the valve housing 16 by the spring force of the spring 33, and the annular protrusion 28b is brought into contact with the flange 16d, thereby increasing the flow area in the flow path P. The flow area is limited to the orifice 28c.

  In this state, when the shock absorber D expands and contracts, the hydraulic oil pushed out from the cylinder 5 through the discharge passage 10 passes through the orifice 28c of the fail valve 4 that has shifted to the fail position and moves to the reservoir 12. A resistance is given to the flow of the hydraulic oil at the orifice 28c, and the pressure in the cylinder 5 is increased, so that a damping force is generated.

  That is, the damping force generated by the shock absorber D at the time of failure is determined only by the resistance provided by the orifice 28c. That is, by setting the flow path area in the orifice 28c to an appropriate value, the damping force at the time of failure can be set, and the flow area of the orifice can be set by the diameter of a single hole. It is possible to obtain a stable damping force as intended without causing large variations in processing.

  As described above, in this damping valve V1, when the valve element 1 and the fail valve 4 are independently driven by a single solenoid S, and the supply current to the solenoid S exceeds a predetermined value, the valve element 1 1 only restricts the flow path P, and the fail valve 4 does not affect the flow path P. On the contrary, when the supply current to the solenoid S is less than a predetermined value, only the fail valve 4 causes the flow path P to Since the valve element 1 is restricted so as not to affect the flow path P, the valve element 1 and the fail valve 4 do not interfere with each other, and the damping force adjustment and the fail safe can be reliably performed. it can.

  Therefore, in order to correct the product-to-product variation due to tolerance or the like, even if the initial load of the spring 3 which is the elastic body that applies thrust to the valve body 2 in the valve element 1 or the spring 17 that is the cutoff elastic body is adjusted, Since the fail valve 4 is not affected and does not affect the damping force at the time of failure, it is possible to eliminate variations in the product during the failure and during normal operation.

  Further, when the supply current exceeds a predetermined value, the solenoid S attracts the fail valve body 28 itself as a movable core, so that it is not necessary to install a separate movable core and the number of parts can be reduced.

  Further, since the spring force adjusting screw 30 as an adjusting member for adjusting the initial thrust force by adjusting the compression length of the spring 3 as the elastic body and the spring 17 as the blocking elastic body is provided, the variation in the damping force for each product is eliminated. Can do.

  In the case of this embodiment, since the movable iron core 27 is interposed between the spring 17 that is a blocking elastic body and the valve body 2, the movable iron core 27 may play in the first fixed iron core 24. In addition, a situation in which abnormal noise is generated due to collision with the valve body 2 or the washer 29 due to the input of vibration is prevented.

  Since the fail valve element 28 includes an orifice 28c that restricts the flow path in opposition to the flow path when the fail position is taken, a configuration is adopted in which a sub flow path having an additional orifice is arranged in parallel with the flow path P. There is an advantage that the structure of the damping valve V1 is not complicated. However, a sub-flow path provided with an orifice is provided in parallel with the flow path P, and a configuration is adopted in which only the sub-flow path functions by blocking the flow path P with the fail valve body 28 at the time of failure. It is not intended to hinder.

  The orifice may be formed by providing a notch at the tip of the annular protrusion 28b of the orifice valve body 28. However, by adopting the orifice 28c formed by the drilling shown in the above-described embodiment, a failure can be achieved. Since variations in damping force can be kept to a minimum, stable damping force as intended can be obtained.

  In addition, the valve element 1 is a poppet valve as described above. However, the valve element is only required to be driven by the solenoid S to adjust the valve opening pressure and the flow path area. It is not limited to poppet valve type. Therefore, for example, it may be configured as a spool valve.

  Next, a damping valve V2 in another embodiment shown in FIG. 5 will be described. The damping valve V2 of the other embodiment is provided with a main valve 40 as a damping force generation source for generating a damping force, and the valve opening pressure of the main valve 40 is controlled by the valve element 1 in one embodiment during normal operation. By adjusting with the fail valve 4 at the time of a failure, the damping force adjustment during the normal operation and the generation of the damping force during the failure are realized.

  Therefore, the damping valve V2 in this other embodiment is different from the damping valve V1 in the embodiment in that the installation of the main valve 40 and a part of the configuration of the valve housing 16 are slightly changed accordingly. Is a point.

  In the description of the damping valve V2 in another embodiment, the same members as those of the damping valve V1 in one embodiment will be described in duplicate, and the detailed description will be omitted only by attaching the same reference numerals.

  Now, different points of the damping valve V2 in the other embodiment will be described in detail. When the left end of the valve housing 16 is fitted to the sleeve 11a of the pipe 11 in the damping valve V1 in the embodiment, this damping valve In the valve V2, an adapter 41 that is screwed into the lateral hole 16a of the valve housing 16 and includes the main valve 40 is fitted into the sleeve 11a.

  As shown in FIG. 5, the adapter 41 includes a large-diameter base 41a fitted into the sleeve 11a, a shaft 41b protruding from the base 41a to the right in FIG. 5, a base 41a and a shaft 41b. A horizontal hole 41c formed so as to pass through, a vertical hole 41d that intersects the middle of the horizontal hole 41c and communicates the lateral hole 41c with the outer periphery of the side portion of the shaft portion 41b, and a vertical hole in the middle of the horizontal hole 41c. A fixed orifice 42 as a fixed valve provided on the discharge passage 10 side to the left of the intersection 41d, a main flow path 43 including a plurality of ports penetrating the base 41a from the left end to the right end in FIG. 5, and a base 41a in FIG. An annular main valve seat 44 formed on the outer peripheral side of the outlet of the main flow path 43 is provided at the right end.

  The shaft portion 41 b is inserted into and screwed into the lateral hole 16 a of the valve housing 16, and is connected to the valve housing 16. The lateral hole 41 c of the adapter 41 is communicated with the lateral hole 16 a of the valve housing 16. . Further, even if the shaft portion 41 b of the adapter 41 is screwed into the lateral hole 16 a of the valve housing 16, the length is set so that the shaft portion 41 b does not interfere with the valve element 1. Thus, in the damping valve V2 in the other embodiment, the flow path P is formed by the horizontal hole 41c of the adapter 41, the horizontal hole 16a of the valve housing 16, and the vertical hole 16b.

  A seal ring 45 is attached to the outer periphery of the base portion 41a of the adapter 41, thereby sealing the space between the sleeve 11a and the discharge passage 10 leading to the reservoir 12 via the outer periphery of the base portion 41a. There is no such thing.

  Subsequently, an annular leaf valve 46 that is a main valve body that opens and closes the main flow path 43 by being seated on and off the main valve seat 44 is laminated on the right end of the base 41a of the adapter 41 in FIG. 5 is sandwiched between the base 41a and the left end of the valve housing 16 in FIG. 5 when the shaft portion 41b is screwed into the lateral hole 16a of the valve housing 16, and the leaf valve 46 has an outer periphery. The leaf valve 46 can be bent as a free end, and the leaf valve 46 is bent by the pressure received from the front side facing the main channel 43 to open the main channel 43.

  Unlike the embodiment, the left end of the valve housing 16 in FIG. 5 is provided with a small-diameter portion 16g. The outer edge of the small-diameter portion 16g determines the fulcrum of the leaf valve 46, and the small-diameter portion 16g A through hole 16h is provided from the outer peripheral side to the lateral hole 16a.

  Further, a flanged cylindrical slider 47 is slidably mounted on the left outer periphery of the valve housing 16 from the flange 16d, and a spring 48 interposed between the flange of the slider 47 and the flange 16d. 5, the left end of the slider 47 comes into contact with the outer periphery of the leaf valve 46, and the leaf valve 46 is urged toward the main valve seat 44 by the urging force of the spring 48 received from the back surface. .

  The slider 47, the leaf valve 46, and the valve housing 16 form an annular back pressure chamber 49 on the side of the small diameter portion 16g of the valve housing 16, and in the middle of the flow path P through the through hole 16h. A pressure (secondary pressure) between the fixed orifice 42 and the valve element 2 in the valve element 1 is introduced into the back pressure chamber 49, and a biasing force by a spring 48 is provided on the back surface of the leaf valve 46. In addition, the secondary pressure also acts in the direction of pressing against the main valve seat 44. The fixed valve may be a choke other than the orifice 42.

  That is, when the shock absorber D is extended or contracted, the pressure in the cylinder 5 acts on the leaf valve 46 from the front side via the main flow path 43, and the secondary pressure and the urging force by the spring 48 from the back side. And the force to bend the outer periphery of the leaf valve 46 to the right in FIG. 5 by the pressure in the cylinder 5 is the bending rigidity of the leaf valve 46 itself, the secondary pressure is applied to the leaf valve 46 When the combined force of the force multiplied by the acting pressure receiving area and the biasing force of the spring 48 is overcome, the spring 48 is compressed, the slider 47 is retracted from the base 41a, the leaf valve 46 is bent, and the main flow path 43 is opened. .

  Note that the seal ring 19 is eliminated so that the movement of the slider 47 is not hindered because the slider 47 is mounted on the outer periphery of the valve housing 16. Further, the slider 47 is biased by the spring 48 even if the slider 47 is retracted by the bending of the leaf valve 46, so that the back pressure chamber 49 is not directly communicated with the reservoir 12. Therefore, the spring 48 only needs to generate an urging force that can prevent the back pressure chamber 49 from communicating with the reservoir 12.

  Here, when the damping valve V2 is normally operated, as shown in FIG. 4, the solenoid S has a current in a range from I2 to I3 that is a current value range exceeding a predetermined value I1, as shown in FIG. To adjust the valve opening pressure of the valve element 2 in the valve element 1, the secondary pressure between the fixed orifice 42 and the valve element 1 in the flow path P is adjusted to the valve opening pressure of the valve element 1. can do.

  In this way, the secondary pressure can be adjusted by adjusting the valve opening pressure of the valve element 1, and by adjusting the secondary pressure acting on the back surface of the leaf valve 46, the main flow path 43 of the leaf valve 46 can be adjusted. The valve opening pressure for opening the valve can be controlled.

  That is, the valve opening pressure in the main valve 40 consisting of the leaf valve 46 and the main valve seat 44, which are the main valve bodies, is adjusted by the amount of current according to the amount of current supplied to the solenoid S. 8 is controlled to the valve opening pressure of the main valve 40, and when the shock absorber D is compressed, the pressure in the cylinder 5 can be controlled to the valve opening pressure of the main valve 40. Specifically, when the supply current to the solenoid S becomes the current value I2, the valve opening pressure in the valve element 1 is minimized and the valve opening pressure in the main valve 40 is also minimized. On the contrary, when the supply current to the solenoid S reaches the current value I3, the valve opening pressure in the valve element 1 is maximized and the valve opening pressure in the main valve 40 is maximized. The damper D generates the maximum hard damping force, and the damping force of the shock absorber D can be continuously adjusted between soft and hard by changing the current supply amount to the solenoid S.

  As described above, in the damping valve V2 according to another embodiment, the secondary pressure is adjusted by applying a thrust according to the current supplied to the renoid S to the valve body 2 to adjust the valve opening pressure in the main valve 40. In order to adjust, the secondary pressure can be adjusted as desired without depending on the flow rate flowing through the flow path P, and even when the expansion / contraction speed of the shock absorber D is in the low speed range, the damping force change with respect to the supply current to the solenoid S changes. Nearly linear, controllability is improved. In addition, since the secondary pressure acting on the back surface of the leaf valve 46, which is the main valve body, is adjusted by applying a thrust according to the current supplied to the renoid S to the valve body 2, the variation in the damping force can be reduced. .

  At the time of failure, since the solenoid S is not energized, the valve element 2 in the valve element 1 is retracted to the right in FIG. 5 by the spring force of the spring 3 against the spring 17 to open the flow path P. On the other hand, the fail valve body 28 in the fail valve 4 is pressed toward the flange 16d side of the valve housing 16 by the spring force of the spring 33, and the annular protrusion 28b is brought into contact with the flange 16d so that the flow area in the flow path P is reduced to the orifice. It will restrict | limit to the flow-path area in 28c.

  In this state, when the shock absorber D expands and contracts, the secondary pressure is determined by the resistance of the fixed orifice 42 and the orifice 28c. If the resistance at the fixed orifice 42 is smaller than the resistance at the orifice 28c, the secondary pressure increases. Conversely, if the resistance at the fixed orifice 42 is greater than the resistance at the orifice 28c, the secondary pressure is reduced. That is, the magnitude of the secondary pressure at the time of failure can be determined by setting the orifice 28c, and the valve opening pressure of the main valve 40 can be arbitrarily set.

  That is, in the damping valve V2, when the damping force of the shock absorber D is adjusted by adjusting the opening pressure of the main valve 40 during normal operation, only the valve element 1 is caused to function with the fail valve 4 being in the open position. On the other hand, when the damping force of the shock absorber D is generated by keeping the valve opening pressure of the main valve 40 constant at the time of failure, the flow path area is limited only by the fail valve 4 without restricting the flow path P by the valve element 1. Try to limit.

  Therefore, in the damping valve V1, the hydraulic oil is mainly passed through the flow path P, and when the normal operation is performed, the valve element 1 and the fail valve 4 at the time of failure are respectively given resistance to generate a damping force. In this case, the hydraulic oil is mainly passed through the main flow path 43, and the damping force is generated by controlling the valve opening pressure of the main valve 40 by the valve element 1 at the time of normal operation and by the fail valve 4 at the time of failure. .

  However, the damping valve V2 in this other embodiment, like the damping valve V1 in one embodiment, independently drives the valve element 1 and the fail valve 4 with a single solenoid S, and connects the solenoid S to the solenoid S. In a state where the supply current exceeds a predetermined value, only the valve element 1 restricts the flow path P, the fail valve 4 does not affect the flow path P, and the valve opening pressure of the main valve 40 is adjusted only by the valve element 1; On the contrary, when the supply current to the solenoid S is less than the predetermined value, only the fail valve 4 restricts the flow path P, and the valve element 1 does not affect the flow path P and increases the valve opening pressure of the main valve 40. Since only the fail valve 4 is set, the valve element 1 and the fail valve 4 do not interfere with each other, and damping force adjustment and fail safe can be performed reliably.

  Therefore, in order to correct the product-to-product variation due to tolerance or the like, even if the initial load of the spring 3 which is the elastic body that applies thrust to the valve body 2 in the valve element 1 or the spring 17 that is the cutoff elastic body is adjusted, Since the fail valve 4 is not affected and does not affect the damping force at the time of failure, it is possible to eliminate variations in the product during the failure and during normal operation.

  Moreover, since the structure similar to 1 embodiment mentioned above is employ | adopted about the structure of the valve element 1, the fail valve 4, and the solenoid S, it obtains the effect similar to the damping valve V1 in 1 embodiment. Can do.

  In addition, in the damping valve V2 in this other embodiment, the secondary pressure is adjusted by applying a thrust according to the supply current to the renoid S to the valve body 2 to adjust the valve opening pressure in the main valve 40. The secondary pressure can be adjusted as desired without depending on the flow rate flowing through the flow path P, and the damping force change with respect to the supply current to the solenoid S even when the expansion / contraction speed of the shock absorber D is in the low speed range. Has an advantage that the controllability is improved and variation in damping force can be reduced.

  Further, the configuration of the damping valve V2 can be realized simply by adding the adapter 41, the leaf valve 46, the slider 47, and the spring 48 to the configuration of the damping valve V1, which is convenient in manufacturing. The valve housing 16 in the damping valve V2 and the valve housing 16 in the damping valve V1 are slightly different depending on the presence or absence of the small-diameter portion 16g and the through hole 16h, but a seal is provided at a site where the slider 47 of the valve housing 16 is mounted in the damping valve V2. If an annular groove is formed so that the ring can be mounted, it can be applied to both the damping valve V1 and the damping valve V2, and it goes without saying that the parts can be made common.

  Since the main valve body in the main valve 40 is a thin leaf valve 46, there is an advantage that the damping valve V2 can be prevented from increasing in size in the axial direction, but it can be opened by the secondary pressure acting on the back surface of the main valve body. As long as the valve pressure can be adjusted, other types of valve bodies such as spools and poppets can be adopted as the main valve body in addition to the leaf valve.

  Further, the solenoid S only needs to be able to drive the valve body 2 and the fail valve 4 in the valve element 1 independently, so the shape, structure, and magnetic path described above are merely examples, and the present invention is not limited thereto.

  This is the end of the description of the embodiment of the present invention, but the scope of the present invention is of course not limited to the details shown or described.

DESCRIPTION OF SYMBOLS 1 Valve element 2 Valve body 2a Large diameter part 2b in valve body Small diameter part 2c in valve body Valve head 3 in valve body 4 Spring 4 as elastic body Fail valve 5 Cylinder 6 Piston 7 Rod 8 Rod side chamber 9 Piston side chamber 10 Exhaust passage 11 Pipe 11a Sleeve 12 Reservoir 13 Outer cylinder 13a Opening 13b in outer cylinder 13c in outer cylinder 14 Step 14 in outer cylinder 15 Suction passage 15 In-cylinder passage 16 Valve housing 16a Horizontal hole 16b in valve housing Vertical hole 16c in valve housing Small inner diameter portion 16d Flange 16e in valve housing Large outer diameter portion 16f in valve housing Through hole 17 in valve housing Spring 18 as blocking elastic body Valve seat 19, 32, 45 Seal ring 20 Case 20a In case Cylindrical portion 20b Bottom portion 20c Case flange 21 Winding 22 Solenoid bobbin 23, 26 Spacer 23a Spacer flange 24 First fixed iron core 25 Second fixed iron core 27 Movable iron core 27a Through hole 28 Fail valve element 28a Fail valve element 28b Annular projection 28c in the fail valve element 28c Orifice 28d in the fail valve element 29 Passage hole 29 in the fail valve element 30 Washer 30 Spring force adjusting screw 30a as adjusting member Spring receiver 31 in spring force adjusting screw Stopper 33 Spring 40 as fail elastic body Main valve 41 Adapter 41a Base portion 41b in adapter Shaft portion 41c in adapter Horizontal hole 41d in adapter Vertical hole 42 in adapter Fixed orifice 43 as fixed valve Main passage 44 Main valve seat 46 Leaf valve 47 as main valve body Slider 48 Spring 49 Back pressure chamber D Buffer P Flow path S Solenoid V1, V2 Damping valve

Claims (13)

  A valve element that is provided in the middle of the flow path and provides resistance to the fluid passing therethrough, a solenoid that applies thrust to the valve body in the valve element in a direction that limits the flow path area, and a maximum flow path area for the valve body In a damping valve provided with an elastic body that gives thrust in the direction, a fail valve arranged in series with the valve element is provided in the middle of the flow path, and the fail valve reduces the open position and flow path area for opening the flow path. A damping valve having a fail position, wherein when the current supplied to the solenoid falls below a predetermined value, the fail position is taken and the valve element and the fail valve are independently driven by a single solenoid.   A fail valve arranged in series independently of the valve element is provided in the middle of the flow path, and when the supply current to the solenoid exceeds a predetermined value, the valve element limits the flow path area of the flow path and the fail valve opens to the open position. 2. The damping valve according to claim 1, wherein when the supply current to the solenoid becomes a predetermined value or less, the valve element opens the flow passage area of the flow passage and the fail valve takes the fail position.   The valve element includes an elastic body that applies thrust to the valve body in a direction that maximizes the flow path area, and a blocking elastic body that applies thrust to the valve body in a direction that restricts the flow path area. The damping valve according to claim 1 or 2, wherein the valve surface valve product is maximized when the value is equal to or less than a predetermined value.   The fail valve includes a fail valve body and a fail elastic body that applies thrust to the fail valve body in the direction of the fail position. When the supply current to the solenoid exceeds a predetermined value, the fail valve body is attracted by the solenoid and opened. The damping valve according to claim 1, 2, or 3, wherein the position is taken.   A main valve that bypasses the flow path, a main valve having a main valve element that opens and closes the main flow path, a fixed valve provided upstream of the valve element and the fail valve of the flow path, and a fixed valve and a valve element in the flow path And a back pressure chamber for biasing the main valve body in a direction in which the main flow path is restricted by the internal pressure while being guided by the internal pressure. Damping valve.   The solenoid attracts the movable iron core at the time of excitation to give a thrust to the valve element in the valve element in a direction to limit the flow path area, and attracts the fail valve element when the supply current exceeds a predetermined value. Item 6. The damping valve according to Item 4 or 5.   3. A margin is provided between a lower limit of a current value supplied to a solenoid for driving a valve element in a valve element during normal operation and a predetermined value for switching a fail valve to an open position. The damping valve according to 3, 4, 5, or 6.   The damping valve according to claim 3, 4, 5, 6, or 7, further comprising an adjusting member that adjusts the compression length of the elastic body and the blocking elastic body to adjust the initial thrust.   9. The damping valve according to claim 3, 4, 5, 6, or 8, wherein the movable iron core is interposed between the cutoff elastic body and the valve body.   The damping valve according to claim 4, 5, 6, 7, 8, or 9, wherein the fail valve body includes an orifice that faces the flow path and restricts the flow path when the fail position is taken.   11. A damping valve according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10, wherein the solenoid adjusts the valve opening pressure of the valve element.   The damping valve according to claim 5, 6, 7, 8, 9, 10, or 11, wherein the main valve body in the main valve is a leaf valve.   The damping valve is provided in the middle of a discharge passage in a shock absorber that discharges fluid from the cylinder to the reservoir through the discharge passage during expansion and contraction. The damping valve according to 8, 9, 10, 11, or 12.

Images